Metalworking machine



Oct. 17, 1944. M. H. ARMS 2,360,462

METALWORKING MACHINE Original Filed Nov. 9, 1940 '7 Sheets-Sheet 1 Oct. 17, 1944.

M. H. ARMS METALWORKING MACHINE Original Filed Nov. 9, 1940 7 Sheets-Sheet 2 Oct. 17, 1944. M. HIARMS 2,360,462

METALWORKING MACHINE Original Filed Nov. 9, 1940 '7 Sheets-Sheet 3 fzwizil- RN Q v \k I p g xv S s g Original Filed Nov. 9. 1940 M. H. ARMS METALWORKING MACHINE '7 Sheets-Sheet 4 Oct. 17, 1944. ARMS METALWORKING MACHINE 7 Sheets-Sheet 5 Origiqal Filed Nov. 9, 1940 OZEQ Oct. 17, 1944. M. H. ARMS METALWORKING MACHINE Original Filed Nov 9, 1940 7 Sheets-Sheet 6 \Q Q E E Q Patented Oct. 17, 1 944 METALWORKING MACHINE Merton H. Arms, Springfield, Vt., assignor to Bryant Chucking Grinder Company, Springfield, Vt., a corporation of Vermont Original application November 9', 194-0, Serial No.

365,071, now Patent No. 2,310,338, dated February 9, 1943. Divided and this application July 14, 1942, Serial No. 450,866

23 Claims.

This invention relates to metal working machines and more particularly to machines for eifecting relative traverse and feed between work and a tool. While in its broadest aspect it is not limited to any particular machine, the invention has been developed more particularly to suit the requirements of internal grinding machines.

One object of the present invention is to provide improved hydraulic actuation of the Various operations of the machine.

A further object is to provide for control of speed and length of stroke of the reciprocating member which supports either the tool or work, by the position of a control member which automatically determines such speed and length of traverse.

A further object is to provide for automatic control of supplemental mechanism in proper time to the reciprocation of the reciprocating,

member, through the position of a control member which determines the particular cycle of operations at any particular time.

Further objects and advantageous constructions will appear from a description of the machine exemplifying the invention shown in the accompanying drawings, in which Figure 1 is a front elevation of an internal grinding machine embodying the invention.

Figure 2 is a fragmentary top plan view of the same.

Figure 3 is a detail sectional view on line 3-3 of Figure 5.

Figure 4 is a detail sectional view on line 44 of Figure 1.

Figure 5 is a fragmentary longitudinal sectional view on line 5-5 of Figure 2.

Figure 6 is a detail sectional view on line 6-6 of Figure 4.

Figure 7 is a detail sectional View on line 11 of Figure 4.

Figure 8 is a fragmentary view, partly in elevation, and partly broken away and in section, of the grinding wheel feed mechanism.

Figure 9 is a view similar to a portion of Figure 2, but to a larger scale.

Figures 10, 11 and 12 are detail sectional views on the correspondingly numbered section lines of Figure 9.

Figure 13 is a detail sectional view on line I3-l3 of Figure 10.

Figure 14 is a diagram of the wheel slide hydraulic drive, the automatic reversing valve being in grind position.

Figure 15 is a view similar to a portion of Figure 14 but with the parts in position for reverse direction traverse.

Figures 16, 17 and 18 are views similar to a portion of Figure 14, but showing the automatic reversing valve in dress, stop, and fast positions, respectively.

As shown best in Figures 1 and 2, the machine may comprise a base I supporting at one end portion a work supporting carriage 5. On the carriage 5 is a support 43 within which is journaled a work-carrying spindle 4! which carries a suitable work supporting chuck 42 at its inner end and belt pulleys 43 at its outer end. The pulleys 43 may be driven by belts 52 passing around them and also around pulleys of a suitable motor (not shown).

The work carriage may be moved transversely of the machine as for positioning and feed. For this purpose the top portion of the machine bed, as shown best in Figure 4, may have secured thereto a bearing within which a nut member BI is rotatably mounted, but held against axialmotion. The nut member 61 has threaded engagement with a lead screw 62. This nut member 6| is shown as provided with a worm wheel portion 83 with which meshes a worm 64 on a shaft 65. When the shaft 65 is stationary, the nut member BI is held against rotation, but rotation of the screw GZmay then be employed to move the work-holding carriage. To this end the lead screw 62 extends through a bearing sleeve 66 secured in abracket member 61 attached by means such as screws 68 to the forward face of the work carriage 5, and to the forward end of this lead screw 62 is keyed a hand feed wheel 10 by which it may be rotated.

Means may be provided for locking the lead screw 62 against rotation and also for producing, when desired, a slow feed rotation thereto. To this end, the lead screw 62 has secured thereto between the bearing bushing 66 and the wheel 10 a worm wheel H, and as shown best in Figures 4 and 6 this worm wheel may be engaged by a worm I2. This worm I2 is carried by a shaft 13 which is journaled longitudinally of a lever 14. This leveris fulcrumed at and by upward rocking of this lever, the worm (2 may be lifted out of contact with the worm wheel 1! as shown in the dotted line position of Figure 6. When so lifted the hand wheel 10 is free to be turned, thus rotating the lead screw 62 for relatively fast motion. 7

When the lever 74 isin the full line position shown in Figure 6 with theworm 'lZ in engagement with the worm wheel H, the lead screw 62 is locked against rotation by means of the wheel 10, but it may be given a slow rotation by rotation of the shaft 13 carrying the worm 12. For this purpose the outer end of the shaft 12 has secured thereto as by a set screw 16 a small hand wheel 11. The lever 14 is mounted in a portion of the bracket 61 and is normally substantially covered by a cover plate 18.

As before noted, motion of the work carriage 5 may be produced by rotation of the nut member 6| by rotation of the shaft 64. As shown best in Figure '1, this shaft 64 is journaled within a sleeve 80 and has keyed to its outer end a hand wheel 8| provided with actuating handles 82. In-

wardly of the hand wheel 8| there is rockably mounted on a bushing 84 within which the shaft 64 is journaled the hub 85 of a bell crank lever having an arm 86 and an arm 81 (see Figures 7 and 8). The arm 81 has pivoted thereto a feed dog 88 adapted to engage the teeth of a ratchet wheel or ring 89 secured to the inner face of the hand wheel 8|, so that by rocking of the bell crank lever a relatively slow intermittent turning of the hand wheel 8I may be produced thus to effect a slow power feed of the work carriage through the slow intermittent rotation of the shaft 66. This feed through rotation of the shaft 64, is, of course, unaffected by the locking of the screw 62 against rotation.

A ring member 90 having a suitable pawl knockoff may be rotatably supported between the ratchet 89 and the back face of the hand Wheel BI and it may be provided with internal teeth meshing with a pinion 92 of a shaft 93 projecting through the hand wheel SI and carrying a knob 96 on its outer end by which it may be turned, thereby to adjust the angular position ofthe knock off ring 90 and thus to determine the extent of feed by rocking of the bell crank lever arm 86. For the purpose of rocking this bell crank, its arm 86 is operatively connected to the upper end of a feed actuating hydraulic plunger 95 working in a cylinder 96 and normally held elevated as by a spring 91. The operation of this feed mechanism will be more fully described in connection with the hydraulic system.

Tool carriage mounting and control The tool herein shown as a grinding wheel I50 is carried by a rotatable shaft I5I journaled in a long quill I52 carried by a wheel head bracket I520 and there may be, if desired, a second tool or grinding wheel I53 carried by a shaft (not shown) journaled in a quill I54 in a second wheel head bracket I55. These brackets are shown as carried by a base I56 which has dovetail connection with a supporting hollow block I51 and support the grinding wheel shafts outwardly of the base I56 allowing a long grinding stroke with rigid support of the grinding wheels. This block I51 is carried by a carriage I58. This carriage is rockably supported by a tube or hollow bar I59 which is slidably and rockably mounted on semi-cylindrical bearing members I8I. Extending into the tube I59 is a shaft I60 provided with an enlarged diameter portion I6I which slidably fits within the tube I59 and forms a piston therefor.

The shaft I60 has reduced diameter end portions I62 and I63. The portion I62 is hollow and through the center thereof passes a pipe I64 which extends into the piston portion I6I and communicates through a port I65 to the interior of the tube I59 to the right of the piston as shown in Figure 5. The space outwardly of the pipe I64 and between it and the inside of the shaft portion I62 communicates through the port I66 with the left hand side of the piston I6I. The shaft portion I63 is solid in cross section and is slidably guided through a sleeve I61 which engages a larger internal diameter portion of the tube I59 and forms a closed end to the pressure cylinder which travels relative to the piston I6I. The right hand end of the tube I59 is open but the left hand end is closed by a bushing I10 having a portion filling the space between the outside of the shaft portion I62 and the inside of the tube I59. A second collar I1I secured against the left hand end of the tube I59 and a reduced diameter portion of the collar I10 completes the closure of this end of the tube I59 to the hollow piston rod portion I62. The inner end of the bushing I10 and the adjacent face of the piston I6I have mating concentric stepped portions which act as a dash pot to cushion the slide motion at the outer limit of its motion.

This tube I59 thus forms a fiuid pressure cylinder, fluid under pressure being introduced into the pipe I64 and discharging through the port I66 and pipe I15 serving to force the tube I59 and the tool carriage carried thereby to the right from the position in Figure 5, while fluid introduced into the space between the pipe I64 and the inside of the shaft section I62 through the pipe I 15 while the escape of fluid is permitted through the pipe I64 acts to move the tool slide to the left or toward the work spindle. The left hand end of the shaft portion I62 extends through a bushing I16 loosely mounted in an end wall member I11 secured as by screws to the machine base I, and on the left hand end of this portion I62 there is positioned a nut I18 which holds the shaft I62 in position. The loose mounting of the bushing I16 prevents cramping of the shaft portion I62, and a yieldable sealing ring I10a prevents the escape of oil around this bushing. The pipe I15 then enters into an opening in an end cap I19 into which also extends the pipe I64 with which communicates a second pipe I80. The right hand end of the tube I59 may be covered by a hood I82 which is telescopically related to a second hood member I83 into which the right hand end of the tube I59 may pass whenthe tool carrier is retracted to its greatestfiextent. A guard or shield I84 secured to the left? hand end of the carriage I58 and having downwardly and outwardly sloping top faces overlying the tube I59 extends beneath the bed I and has transversely extending top ribs for directing foreign matter laterally.

The carriage I58 and the member I82 are provided with a pair of spaced inclined ways I 85 and I86, respectively, on which may be adjustably supported a pair of slides I61 and I88 which support between them belt tightener pulleys I89 and I90. These pulleys engage belts I91 and. I92, respectively, which pass over a driving pulley I93 of a driving motor I94 and over pulleys, I95 and. I96 on the grinding wheel shafts I5I and one (not shown) journaled within the quill I54, respectively. The motor I94 is carried by'the tool carriage as shown in Figure 3, beingbolted to the lower face thereof, so that it partakes of the motion of this carriage and remains in the same relation to the grinding wheel pulleys I95 and I96 at all times.

The tool carriage extends rearwardly of the tube I59 which rockably supports it and as shown in the parent application Serial No. 365,071, filed November 9;, 1940, now Patent No. 2,310,338, granted February 9, 1943, for Metal working machine, of which the present application is a division, means may be provided for controlling the angular position of the tool carriage about the axis of the tube I59. As this mechanism forms no part of the present invention, however, it is not illustrated herein.

Tool carriage traverse mechanism The hydraulic mechanism for efiecting traverse and control of the tool carriage is shown in detail in Figures to 14, inclusive. Referring first to Figure 14, at 350 is shown a tank having a liquid such as oil which is employed to drive the tool carriage, being supplied and discharged through the pipes I and I80 shown in detail in Figure 4 as previously described. The movable cylinder I59 is indicated diagrammatically in Figure 14, this cylinder supporting the tool carriage. Liquid is pumped from the tank 350 by the pump I into the pipe 352. A limiting pressure valve 353 communicating with the pipe 352 and discharging to the tank 350 through the pipe 354 acts to maintain pressure in the pipe 352 at the desired amount. This pipe 352 leads to a valve casing 3540 within which is positioned a pilot valve 355 and a reversing valve 356. It also leads through the pipe 351 to a valve casing 358 containing an operator actuable controlling valve 359 and a shut off valve 360, which may be actuated at suitable times to cut out the automatic valve within the casing 3540 when hand control of the traverse is desired; In the position shown in Figure 14 for automatic grinding traverse, liquid under pressure passes from the pipe 352 through the passages 365 and 368, the valve port 369, to the pilot valve, through the longitudinal passage 31I in this valve, through the port 312, the passage 313 and the passage 314, through the check valve 3130 and throttle valve 313I and finally also through port 3132 to the left end of the reversing valve 366, thus forcing the reversing valve 356 into the position shown,

hand end of this valve first through the pipes 438 and 439 and later through the pipe 439 only when the valve closes the port 4310, the throttle valve 4390, passage 438, port 431, through the valve passage 435, port 31, passage 443 and pipe 444 to the discharge pipe 4I9. A check valve 439I in the pipe 439 prevents free discharge through the pipe 439 so that the rate of flow and thus the rate of motion of the reversing valve near the end of its stroke is determined by the setting of the throttle valve 4390. This adjustment of the speed of motion of the reversing valve allows for a sharp control of the cut off for the tool slide so that the slide is stopped at a definite point. In this position of the reversing valve, fluid under pressure around the neck 366 of the reversing valve may pass through the passage 315 around the neck 316 of the valve 360, port 311, around the neck 318 of the hand operated valve 359 and out through the port 319 to the pipe I15, thus forcing the cylinder I59 to the left. The discharge from the opposite end of the cylinder takes place through the pipe I80, the port 38!], around the neck 38I of the manual control valve 359, through the port 382, around the neck 383 of the valve 360, through the pipe 385, through the port 386, around the neck 381 of the reversing valve, through the port v the fluid under pressure escaping from the right 388 and passage 389, the port 390 of the pilot having two ports 396 and 391 therearound. The port 396 is a restricted port, the extent of opening of which may be adjusted by turning the valve 395, thus to determine the rate of discharge of fluid from the cylinder I59 and thus to determine the traverse rate. The port 391 is always 'Wide open until after port 396 is wholly closed,

but in grinding position no liquid passes therethrough as will later appear. The parts in this figure are in the grinding condition during which the port 396 allows the discharge through the pipe 398 into the port 399 of the manual control valve 400 which is vertically movable to any selected-of four positions in any of which it may be yieldably retained as by a ball detent 40I shown in Figure 10, and determines in order whether the control is set for grinding, dressing, stop or fast speed.

In Figure 12 these four positions, grinding, dressing, stop and fast speed are shown indicated by the corresponding angular positions in a vertical plane of a control handle 488' which carries a mutilated gear 402 meshing with a pinion 403, which, in turn, meshes with a rack portion 404 and the valve 400. This valve is also permitted a rocking motion, this for the purpose of controlling the axial position of the pilot valve 355, one end of which is formed as a rack bar 405 with which meshes a gear 406 on the lower end of the valve 400. The rocking motion of this valve 400 does not, however, affect in any way its control of its valve ports and the handle 408 rocks with it in a horizontal plane.

In the grinding position shown for this valve 400 in Figure 14, the discharge from the pipe 398 and the port 399 passes around the valve 400 to the pipe 4I3, around the valve neck M0 and through the port M2 and pipe 4I4, both pipes M3 and M4 leading to a valve casing 4I5 within which is a rockable valve M6. The pipe M3 is always open to the pipe 398 through an annular passage around the outside of the valve 400 regardless of the position of the valve 400. The valve MS has a pair of ports 4" and M8, both of which, in the position shown in Figure 14, communicate with the discharge pipe 4I9 leading back to the tank 350. Beside passing through the pipe 398 to the valve 400 there is also a by-pass discharge from the pipe 398 through an adjustable restricted rocker valve 420 having the V port 42I, through the pipe 422, the port 423 of the valve 400, which also leads around the neck 4I0 of this valve from which the discharge takes place, as previously described. The port 391 of the adjustable valve 395 leads through a pipe 426 to a port 421 of the valve 400, but in this position of the parts, this port 421 is closed by the part 428 of the valve 400 so that in grind position the traverse speed is controlled by the extent of opening of the port 396 of the valve 395. The pilot valve is also forced fully to its right hand position by a load and fire hydraulic means, since as soon as this valve has been moved far enough to open the valve passage 31I to pressure, this pressure acts on the left hand face of the valve shoulder 3550 while the shoulder 355i at the right hand end of the pilot valve is open to discharge through the valve passage 435.

When the tool carriage approaches the left hand end of its travel, a dog 430 thereon engages the head 43I of the valve 490 and continued motion of the carriage rocks the valve 409 and moves the pilot valve 355 axiallytoward the positionshown in Figure 15 to which it is forced by valve passage 31! has been moved out of registry with the port 369 and a valve passage 435 placed in registry therewith, thus permitting the fluid under pressure to pass through this passage 435 through the valve passage 436 and the port 431, the passage 438, and the passage 439 to the right hand end of the reversing valve 356, thus driving the reversing valve to the left to the position shown in Figure 15, while the left hand end of the reversing valve discharges through the pipe 314, the passage 313, the valve port 448- around the neck 44! of the pilot valve through the valve passage 31!, the port 442, passage 443, and pipe 444 to the discharge line 4I9. With the reversing valve in this position, fluid under pressure passes from the pipe 352 and port 365 around the neck 381 of the reversing valve, port 386 to the pipe 385 leading to the manual traversing valve casing, around the neck 383 of the valve 369, passage 382, around the neck 38! of the hand control valve, and through the pipe I88 to the power cylinder I59 to drive the carriage in the reverse direction or to the right, the discharge taking place through the pipe I15, past the neck 318 of the hand control valve, neck 316 of the valve 388, the passage 315, around the neck 366 of the reversing valve, through the port 445, passage 446, port 441, around the neck 39!, through pipe 393, past the valve 395 and from thence back around the valve 499 and through the valve 4I6 to discharge. This takes place until the dog 448 impinges on the valve 498 and rocks it back toward its initial position to which it is forced by the hydraulic load and fire mechanism previously described, whereupon the cycle is repeated. It will be noted that neck 39! of the pilot valve is provided with conical ends which effect initial and final throttling through the ports controlled thereby, thus slowing the traverse before reversing and returning.

In the dress position the valve 488 is lowered to the position shown in Figure 16 in which it is too low to be affected by the dog 448 so that the tool carriage is permitted an extended outward traverse at which time the dog 449 becomes effective to reverse the traverse at one end while the dog 438 is still in effective relation at the other end. From an inspection of Figure 16 it will be seen that in this position of the valve 400 it shuts 011 port 399 from around the neck 4!!! and the discharge through the pipe 4i4', but does not prevent flow from this port around the valve to the pipe 4 I3. This permits the tool'slide to retract and remove the wheel from the work at normal traverse speed until the wheel approaches dress position, whereupon the dog 455 engages the rabbit ears 496 and shuts oil the valve port 4I1 while leaving open the port 4I8. All the discharge is then forced to take place through the throttle valve 42!, pipe 422, around the valve neck 4!!! and through pipe 4I4, so that the outward travel of the wheel carriage is slowed for dressing. The wheel, therefore, comes out of. the hole in the work and returns at grinding speed, but its traverse is slowed during the truing portion of its extended traverse. Automatic reversal of this extended stroke is produced by the dog 449, turning the valve 408.

On depressing the handle 408 to the stopposition indicated in Figure 12, the valve 400 is brought into the position shown in Figure 17. In this position of the valve, it will be noted that there is open communication through ports 455 and 456 between the pipes 451 and 458. These pipes communicate with the pipes 385 and 315, respectively, which in the inoperative position of the hand traverse valve 359, communicate with the pipes I15 and I88 which lead to opposite ends of the power cylinder I59. The pressures in opposite ends of the cylinder I59 are thus balanced and the wheel slide stops. The tool carriage may now be moved freely by hand or by actuation of the hand traverse mechanism, which, as will later be shown, shuts off the pipes 315 and 385 from the cylinder I59. In all of the positions of the valve 496, except the stop position, the pipes 451 and 458 are cut off from each other bysuitable parts of the valve 400.

Further depression of the handle 40! bringing the valve 489 into fast position is shown in Figure 18. In this position of the valve 400 the discharge port 423 is closed, but the unrestricted discharge pipe 426 is open through the port 421 and around the neck 4I8 of the valve 400 through the discharge pipe 4I4, thus permitting unrestricted discharge of fluid from one or the other side of the power cylinder I59, depending upon the setting of the reversing valve. In this position of the parts, also, the top of the valve 4!!!! is lowered to a point where it is unaffected by the stop 449 so that the traverse mayv be further extended in an outward direction. The stop 436 is long enough to reverse the traverse at the inner end of its stroke automatically.

The stop dog 465 which controls the angular position of the valve 4I6 is fixed to a block such as 5 I I3 adjustable within a T slot 5! I in a bracket 5I2 secured to the tool carriage, as best shown in Figure 3, while the dogs 436, 448, and 449 are similarly secured in an under cut groove 5I3 of the same bracket 5I2. As shown best in Figures 9 and I2, the handle 498 may be rocked angularly by hand in a horizontal plane to turn the valve 408, thus to eifect reversal of the direction of traverse at will.

Hand traverse control As before mentioned, the traverse may be controlled by the operator by a manual control of the valve 359, actuation of this valve for such control serving automatically to cut out the automatic traverse control. In the inoperative position of the hand control, the parts being in the position of Figures 10 and 14, a hand lever 415 is in vertical position, this lever as shown in Figure 14 being pivoted to a link 416, which, in turn, is pivoted to an ear 411 on the cap 418 closing the end of the valve casing 358. The lower end of the hand lever 415 is pivoted at 480 to a rod 48! extending from one end of the valve 359. In Figure 10 a slightly different mounting of the hand lever 415 is shown in which it is fulcrumed on a fixed pivot 415a and its lower end engages between flanges of a spool 4151) carried by the valve rod 48I. At each end of this valve 359 is positioned a spring centering device, this comprising a pair of spring seat members 482 and 483. The seat member 482 isperforated for the passage of the rod 48! and is normally pressed against an end shoulder 484 of the valve by a spring 485 seated in a socket 486 in the cap 41.8. The spring seat483 normally engages the opposite end of the valve 359 and isv spring pressed by a spring 488 seated in a socket 489 in the end wall member 499 of the valve casing 358. Both of these spring seats 482 and 483 are limited in their inward motion by annular shoulders 499 and 49I, respectively, at the ends of the valve casing 358, By pulling the handle 415 outwardly toward the dotted line position shown in Figure 14, the valve 359 is moved to the right against the pressure of the spring 488, this causing the left hand edge of central valve portion 495 to uncover the port 496 to which the pressure pipe 351 leads from the pressure pipe 352. This allows fluid under pressure to pass directly from the port 496 to the port 319 and to the power cylinder I59 through the pipe I15, while its shoulder 491 uncovers the port 498 leading to the discharge pipe 499, thus opening up the opposite pipe I89 from the power cylinder I59 to discharge, thus causing the cylinder I59 to be moved to the left. At the same time fluid under pressure from the port 496 passing around the valve neck 318 escapes through the passage 599 to the left end of the valve 369, driving it to the right against the pressure of the spring 59I reacting against its right hand end, and shuts ofl passages leading to the pipes 315 and 385, thus cutting off the automatic traverse mechanism. On moving the lever 415 inwardly toward the right hand dotted line position of Figure 14, the valve 359 is moved in the reverse direction, opening up the port 496 at the right hand end of the valve port 495 and connecting through the port 389 directly to the pipe I89 leading to the opposite end of the power cylinder I59 so that this power cylinder is driven to the right, the discharge taking place through the pipe I15. passage 319, passage 592 to the discharge pipe 499. Likewise the fluid under pressure may then pas around the neck 38I of this valve through the passage 599 tothe left hand end of the valve 369, thus driving this valve 369 in the same direction as before and cutting oil the pipes 315 and 385. The traverse is thus in the reverse direction, but as before the automatic traverse mechanism is out 01f by the same position of the valve 369. It will be noted that the valve portion 495 has tapered ends so. that the port 496 is opened or closed gradually on motion of this valve. Thus the speed of traverse as controlled by this valve depends on the extent of its displacement so that the further the handle 415 is moved from its central position, the faster is the speed of traverse of the wheel slide.

Power cross feed The power cross feed which actuates the plunger 95 is operative only when the valve 499 is in grinding position, in which position only, the pipe 559 leading from a port 55I of the casing of the valve 499 is open to fluid under pressure through port 552 and pipe 553 from the port 369 of the pilot valve, around the neck 554 of the valve 499. This establishes hydraulic pressur in the pipe 559 regardless of the direction of traverse of the wheel and leads to the two cylinders 555 and 556 (see Figure 14) containing the piston valves 551 and 558, respectively. In the positions shown in Figure 14 with th plunger 95 in its upper position and with both of the pistons 551 and 558 in the lowered positions shown, fluid pressure from the pipe 559 may pass around the neck 559 of the valve 558 out through the pipe 569 above the piston of the plunger 95 so as to force this plunger downwardly and effect a feeding oscillation .to the bell crank feed lever. At the same time fluid under pressure in the pipe 569 passing the throttle valve 56I builds up pressure above the piston valve 562 slidable in a cylinder 563, forcing this valve downwardly, fluid under pressure escaping from beneath the valve 562 through the pipe 566', around the neck 561 of the valve 558, and through the discharge pipe 568. When the valve 562 is driven downwardly to a sufiicient distance, it opens connection to the fluid pressure above it through the pipe 569 beneath the piston valve 551 while fluid escapes from above this valve 551 through the pipe 513, around the valve neck 564 to the return line 565, thus raising this valve 551, permitting fluid to pass from the pipe 559 around the neck 519 of the valve 551 and the pipe 51I beneath the valve 558 while discharging from above the valve 558 through the pipe 5589, around the neck 5519 of the valve 551 to the discharge pipe 512. 558, shutting off the connection from the pipe 559 to the pipe 569 and. opening the pipe 569 to the pipe 512 which leads to the discharge. This allows the spring 91 to lift the plunger 95 and permits the slow escape of fluid under pressure through the throttle valve 56I from above the valve 562 past the neck 559 and pipe 512 to discharge. This position of the valve 558 opens connection from the pressure pipe 559 past the neck 561 of the valve 558. through the pipe 596 and beneath the valve 562, lifting this valve. As soon as the valve 562 is raised sufficiently, fluid under pressure beneath this valve passes through the pipe 513 to the upper end of the cylinder 555 and so forces the piston 551 downwardly, fluid under pressure escaping from beneath the valve 551, through the pipe 569, around the neck 564 of the valve 562, and out through the discharge pipe 565. These various discharge pipes from this mechanism may, of course, lead to a common discharge pipe passing to the fluid pressure tank. It will thus be seen that whenever the valve 499 is in grind position and in that position only, there is an intermittent feed produced, depending for its speed of action on the setting of the throttle valve 56I which controls the rate of motion of the valve 562.

From the foregoing description of an embodiment of this invention it should be evident to those skilled in the art that changes and modifications may be made without departing from the spirit or scope of this invention.

I claim:

1. In combination, a, traversing carriage, power means for traversing said carriage including an axially movable and rockable control member, means responsive to the angular position of said member for determining the direction of traverse of said carriage, elements carried by said carriage in position to impinge on said member and rock said member as said carriage traverses to reverse the direction of traverse at traverse limits dependent at least in part on the axial position of said member, and means controlled by said member in accordance with its axial position for determining the speed of traverse.

2. In combination, a traversing carriage, fluid pressure means for traversing said carriage including an axially movable and rockable control valve, means responsive to the angular position of said valve for determining the direction of traverse of said carriage, elements carried by This lifts the valve said carriage in position to impinge on said valve and rock said valve as said carriage traverses to reverse the direction of traverse at traverse limits dependent at least in part on the axial position of said valve, and means controlled by said valve in accordance with its axial position for determining the speed of traverse.

3. In combination, a traversing carriage, power means for traversing said carriage including an axially movable and rockable control member, means responsive to the angular position of said member for determining the direction of traverse of said carriage, elements carried by said carriage in position to impinge on said member and rock said member as said carriage traverses to reverse thedirection of traverse at traverse limits dependent at least in part on the axial position of said member, a second carriage, means for producing relative motion between said carriages transverse to the line of traverse of said traversing carriage, and means controlled by said member in accordance with its axial position determining whether or not said producing means will be operative.

4. In combination, a traversing carriage, fluid pressure means for traversing said carriage including an axially movable and rockable control valve, means responsive to the angular position of said valve for determining the direction of traverse of said carriage, elements carried by said carriage in position to impinge on said valve and rock said valve as said carriage traverses to reverse the direction of traverse at traverse limits dependent at least in part on the axial position of said valve, and means controlled by the axial position of said valve for determining the control of speed of traverse, a second carriage, means for producing relative motion between said carriages transverse to the line of traverse of said traversing carriage, means controlled by said member in accordance with its axial position determining whether or not said producing means will be operative.

5. In combination, a traversing carriage, power means for traversing said carriage including an axially and rockably movable member having an end portion extending toward a portion of said carriage, means controlled by said member in accordance with its angular position determining the direction of traverse, elements carried by said carraige and projecting by diiferent amounts therefrom in position to strike and rock said member end portion depending upon the axial position of said member and thus defining limits of carriage traverse dependent on the positions of the elements projecting sufficiently to strike and rock said member at any selected axial position of said member, and means for adjusting the axial position of said member.

6. In combination, a traversing carriage, fluid pressure means for traversing said carriage including an axially and rockably movable valve having an end portion extending toward a portion of said carriage, means controlled by said valve in accordance wtih its angular position determining the direction of traverse, elements carried by said carriage and projecting by different amounts therefrom in position to strike and rock said valve end portion depending upon the axial position of said valve and thus defining limits of carriage traverse dependent on the positions of the elements projecting sufficiently to strike and rock said valve at any selected axial position of said valve, and means for adjusting the axial position of said valve.

'7. In combination in a machine having a grinding wheel carrying traversing carriage, power means for efiecting traverse of said carriage, a member for controlling said power means, elementscarried by said carriage in position to move said member adjacent to desired traverse limits to cause said member to control said traversing means to reverse the direction of traverse, said member having a grinding position and a dressing position, in which dressing position one end limit element operative in grinding position is inoperative thereby permitting an extended stroke of said carriage, a low speed limiting device for said power means, and means carried by said carriage effective when said carriage enters said extended stroke to actuate said device to slow the speed of traverse in said extended stroke to a speed suitable for wheel truing.

8. In combination in a machine having a grinding wheel carrying traversing carriage, hydraulic means for effecting traverse of said carriage, a valve for controlling said hydraulic means, elements carried by said carriage in position to move said valve adjacent to desired traverse limits to causesaid valve to control said hydraulic means to reverse the direction of traverse, said valve having a grinding position and a dressing position, in which dressing position one end limit element operative in grinding position is inoperative thereby permitting an extended stroke of said carriage, a low speed limiting device for said hydraulic means, and means carried by said carriage efiective when said carriage enters said extended stroke to actuate said device to slow the speed of traverse in said extended stroke to a speed suitable for wheel truing.

9. In combination in a machine having a traversing carriage, hydraulic means including a hydraulic power cylinder connected to said carriage foreffecting traverse of said carriage, an axially movable and rockable valve controlling said hydraulic means, the angular position of said valve determining the direction of traverse, elements carried by said carriage positioned to turn said valve from one to another angular position at the desired limits of traverse for reversing supply and discharge connections to said cylinder to reverse the direction of traverse, said valve having a plurality of axial positions in one of which positions said hydraulic means is conditioned to produce traverse of said carriage and in another of which positions both ends of said cylinder are in communication with each other so that the traverse stops and said carriage is free to be moved in either direction.

10. In combination in a machine having a traversing carriage, hydraulic means including a hydraulic power cylinder connected to said carriage for effecting traverse of said carriage, an axially movable and rockable valve controlling said hydraulic means, the angular position of said valve determining the direction of traverse, elements carried by said carriage positioned to turn said valve from one to another angular position at the desired limits of traverse for reversing supply and discharge connections to said cylinder to reverse the direction of traverse, said valve having a plurality of axial positions in one of which positions said hydraulic means is conditioned to produce traverse of said carriage with restricted hydraulic flow to produce a working speed of traverse, and in another of which axial positions said hydraulic means is conditioned to traverse said carriage without such flow restriction to produce a high speed idle carriage traverse.

11. In combination in a machine having a traversing carriage, hydraulic means including a hydraulic power cylinder connected to said carriage for eflecting traverse of said carriage, an axially movable and rockable valve controlling said hydraulic means, the angular position of said valve determining the direction of traverse, elements carried by said carriage positioned to turn said valve from one to another angular position at the desired limits of traverse for reversing supply and discharge connections to said cylinder to reverse the direction of traverse, said valve having a plurality of axial positions in one of which positions said hydraulic means is conditioned to produce traverse of said carriage with restricted hydraulic flow to produce a working speed of traverse, and in another of which axial positions said hydraulic means is conditioned to traverse said carriage without such flow restriction to produce a high speed idle carriage traverse,"one of said elements being out of operative relation to said valve when said valve is in said other axial position, whereby the traverse of said carriage in one direction is extended out of con trol of said elements.

12. Carriage moving means comprising a reciprocable member, hydraulic means for moving said member in one direction, said hydraulic means including mechanism automatically releasing the fluid pressure on motion of said member to a predetermined point and. for re-establishing fluid pressure on return of said member to starting position, means efiective to return said member to starting position when said pressure is released, and means operative on motion of said member in one direction and connecting said reciprocable member and carriage to cause motion of said member to feed said carriage.

13. Carriage moving means comprising a reciprocable member, hydraulic means for moving said member in one direction, said hydraulic means including mechanism automatically releasing the fluid pressure on motion of said member to a predetermined point and for reestablishing fluid pressure on return of said member to starting position, means effective to return said member to starting position when said pressure is released, said hydraulic means including a device for adjusting the rate of flow of fluid to act on said member, and means operative on motion of said member in one direction and connecting said reciprocable member and carriage to cause motion of said member to feed said carriage.

14. In combination in a machine having a traversing carriage, power means for effecting traverse of said carriage, a member for controlling such power means, elements carried by said carriage in position to move said member adjacent to desired traverse limits and cause said member to control said traversing means to reverse the direction of traverse, an operator movable member, and connections from said operator movable member to said power means causing one motion of said operator movable member to operatively disconnect said controlling member from said power means and another motion of said operator movable member to control said power means to cause said carriage to be traversed in either selected direction.

15. In combination in a machine having a traversing carriage, fluid pressure means for effecting traverse of said carriage, a valve for controlling such power means, elements carried by said carriage in position to move said member adjacent to desired traverse limits and. cause said valve to control said traversing means to reverse the direction of traverse, an operator movable valve, and connections from said operator movable valve to said fluid pressure means causing one motion of said operator movable valve to operatively disconnect said controlling valve from said power means and another motion of said operator movable valve to control said fluid pressure means to cause said carriage to be traversed in either selected direction.

16. In combination in a machine having a traversing carriage, power means for traversing said carriage, automatically acting means controlling said power means by theposition of said carriage to reverse the direction of traverse at desired traverse limits, an operator actuable member for controlling said power means to reverse the direction of traverse of said carriage, said operator actuable member having operative connections to said automatically acting means to render said automatically acting means inoperative before said operator actuable member may be made efiective to control said power means.

17. In combination, a traversing carriage, power means for traversing said carriage, automatically acting means controlling said power means to reverse the direction of traverse of said carriage at desired traverse limits, other control means for said power means, operator actuated means for actuating said other control means to actuate said power means to move said carriage, and means controlled by said other control means for rendering inoperative said automatically acting control means on actuation of said operator actuated means to control said other control means. and to render operative said automatically actingmeans on actuation of said operator actuated means to stop the action of said other control means.

18. In combination, a traversing carriage, fluid pressure means for traversing said carriage including fluid pressure actuated controlling valves, means controlled by saidcarriage for controlling fluid pressure to actuate said controlling valves for automatically reversing the direction of traverse at desired traversing limits of said carriage, an operator actuable valve for controlling the supply and discharge of fluid pressure to and from said traversing means, and means actuated by said operator actuable valve to cut out said pressure actuated valve before said operator actuable valve can control the supply and discharge of fluid under pressure to and from said fluid pressure carriage traversing means.

19. In combination, a traversing carriage, fluid pressure means for traversing said carriage including fluid pressure actuated controlling valves, means controlled by said carriage for controlling fluid pressure to actuate said controlling valves for automatically reversing the direction of traverse at desired traversing limits of said carriage, an operator actuable valve for controlling the supply and discharge of fluid pressure to and from said traversing means, and means actuated by said operator actuable valve to cut out said pressure actuated valve before said operator actuable valve can control the supply and discharge of fluid under pressure to and from said fluid pressure carriage traversing means, said operator actuable valve having throttling ports to control by the position of said operator actuable valve the speed of carriage traverse.

20. In combination, a traversing carriage, power means for traversing said carriage comprising a pair of valves each movable axially to cover and uncover ports spaced axially of its respective valve, one of said valves being rockable about its axis, connections from said rockable valve to the other of said valves causing the rocking of said rockable valve to move said other valve axially, means controlled by said other valve in accordance with its axial position by selection of covered and uncovered ports to determine the direction of traverse of said carriage, means controlled by said rockable valve in accordance with its axial position to determine the speed of traverse of said carriage, and elements carried by said carriage in position to impinge upon and rock said rockable valve at desired limits of traverse determined by the axial position of said rockable valve.

21. In combination, a traversing carriage, power means for traversing said carriage comprising a pair of valves each movable axially to cover and uncover ports spaced axially of its respective valve, one of said valves being rockable about its axis, connections from said rockable valve to the other of said valves causing the rocking of said rockable valve to move said other valve axially, means controlled by said rockable valve in accordance with its axial position by selection of covered and uncovered ports to determine the direction of traverse of said carriage, a feed carriage, means for feeding said feed carriage transverse to the direction of traverse of said traversing carriage, means controlled by said rockable valve in accordance with its axial position to determine Whether or not said feeding means is operative, and elements carried by said carriage in position to impinge upon and rock said rockable valve at desired limits of traverse determined by the axial position of said rockable valve,

22. In combination, a traversing carriage,

power means for traversingsaid carriage comprising a pair of valves each movable axially to cover and uncover ports spaced axially of its respective valve, one of said valves being rockable about its axis, connections from said rockable valve to the other of said valves causing the rocking of said rockable valve to move said other valve axially, means controlled by said other valve in accordance with its axial position by selection of covered and uncovered ports to determine'the direction of traverse of said carriage, a feed carriage, means for intermittently feeding said feed carriage at predetermined intervals transverse to the direction of traverse of said traversing carriage, means controlled by said rockable valve in accordance with its axial position to determine whether or not said feeding means is operative, and elements carried by said carriage in position to impinge upon and rock said rockable valve at desired limits of traverse determined by the axial position of said rockable valve.

23. In combination, a traversing carriage, power means for traversing said carriage comprising a pair of valves each movable axially to cover and uncover ports spaced axially of its respective valve, one of said valves being rockable about its axis, connections from said rockable valve to the other of said valves causing the rocking of said rockable valve to move said other valve axially, means controlled by said other valve in accordance with its axial position by selectionof covered and uncovered ports to determine the direction of traverse of said carriage, elements carried by said carriage in position to impinge upon and rock said rockable valve at desired limits of traverse determined by the axial position of said rockable valve, and means controlled by said rockable valve at one axial position to rendersaid traversing means inoperative and said carriage free to be traversed out of control of said power traversing means.

MERTON H. ARMS. 

